JP2003535275A - Hydraulic shock / pressing device - Google Patents

Abstract

The present invention relates to a hydraulic DEVICE having a valve housing (1) with a movable valve body (2) arranged inside the valve housing, a hydraulic cylinder with at least a hydraulic chamber (115), and at least a control mechanism (4) for the control of said movable valve body (2), the valve body (2) is substantially sleeve-shaped and arranged inside an annular space (128) in the valve housing (1), and said valve body (2) is provided with a plurality of apertures (250, 251, 252; 206, 202) to make a flow of hydraulic liquid possible in the radial direction through the valve body (2).

Description

Detailed Description of the Invention

TECHNICAL FIELD The present invention controls a valve housing having a movable valve body arranged inside a valve housing, at least one hydraulic chamber provided inside the valve housing, and the movable valve body. And a valve housing comprising a plurality of combined elements, at least two of which are coaxially arranged with respect to each other. An annular space is formed between the parts and the valve body is substantially sleeve-shaped and is arranged inside the annular space of the valve housing, the valve body being provided with a plurality of openings for passing through the valve body. To allow the hydraulic fluid to flow radially.

BACKGROUND OF THE INVENTION In many known applications, it is necessary to carry out an immediate impact movement and / or a controlled movement during the transmission of heavy forces (oil Certain hydraulic systems are often suitable (when pressure transmission is used). According to the background art, such a hydraulic system is controlled / regulated by a servo valve suitable for high flow of oil at high pressure, which means that the valve is very expensive. Furthermore, it forms its own unit at a distance from the hydraulic system. This is often a problem in servovalves with large outer dimensions, so it is very bulky and can weigh hundreds of kilograms. Moreover, hydraulic hoses often have to be used between the servo valve and the hydraulic system, which means that there is a high risk of damage to itself. It can be said that it is difficult to meet the requirements of quickness and high accuracy in the compressibility of the hydraulic hose because of the large oil flow at high pressure. Moreover, such servovalves require relatively long adjustment times, often up to 100 milliseconds, which is unsatisfactory for many applications.

An application where long adjustment times are unsatisfactory is impact pressing. Impact pressing is known, for example, from US Pat. No. 3,965,799, US Pat. No. 4,028,995 and US Pat. No. 4,635,531, which show alignment with immediate adjustment. The hydraulic piston is part of the valve function. As a result, the function of the hydraulic piston cannot be freely controlled and its function is connected to the position of the hydraulic valve inside the valve housing. Therefore, with respect to the field of application, the device is limited to a linear hammer vibrating machine, which moves instantly between two positions and has no possibility to control between them as a whole.

The above-mentioned known types of impact pressing are not suitable for forming using high kinetic energy, which is due to certain forms such as cutting and punching, forming metal components, powder compaction and similar operations. It is a material treatment, where the initial impact is significant and the speed of the pushing piston may be 100 times or more faster than conventional pushing. This fact places a very high demand on the valve arrangement and it must be possible to carry out very fast adjustments of large flows, while the hydraulic system must be able to deploy high forces properly. There is high pressure. The operating principle is based on the production of very high kinetic energy in the short term. It is not uncommon for the power of a percussion piston to reach at least 20-30 KN with an impact shock of average size upon acceleration. In order to make such a machine marketable, it is desirable to provide a rigorous construction while at the same time providing a valve assembly that is less expensive and requires less space.

The condition for achieving such a valve function is to provide a sleeve-shaped valve body between the two coaxial parts of the valve housing, which thus forms an annular space in which A sleeve-shaped valve body is provided. Although the above basic principles are in fact known from U.S. Pat. No. 4,559,863, the above mentioned publications in principle refer to stamp hammers which use hydraulic techniques only to lift the hammer. The only pressure that drives the hammer downwards is the residual pressure, which accumulates in the low pressure accumulator after an immediate return. In such devices, gravity, rather than hydraulic technology, performs the essential maneuver for impact. Therefore, such a structure is not suitable for forming using high kinetic energy, which requires very high acceleration. Another disadvantage of the known device is that the adjustment cannot be done immediately. Furthermore, the function of the hydraulic piston cannot be controlled independently of the position of the hydraulic piston. Furthermore, the known device is not balanced against the forces acting in the radial direction, which mercilessly causes problems when very high hydraulic pressures are applied.

It will be appreciated that the application described above is only one of many fields of application and that there are substantial opportunities for improvement with respect to the valve assembly and its mode of operation. Therefore, many of the problems identified in relation to shock pressing are also found in many other areas of operation, and it is important to try to find some solution to the problem, or at least to the identified problem. It is clear that there is. An example of such another area is hydraulic regulation means, which according to the servo valve assembly described above is today an expensive and / or very cumbersome solution and / or time. It is often a costly device.

DISCLOSURE OF THE INVENTION It is an object of the invention to eliminate or at least minimize the problems mentioned above, which is achieved by the hydraulic system according to the above description. This is due to the fact that the valve body is located inside the valve housing and is adjacent to the opening, in such a way that it essentially preferably and generally balances against the radial acting hydraulic pressure. An edge portion is provided on both the inner and outer surfaces of the valve body, the edge portion interacting with an edge portion and a channel located inside the valve housing. As such, hydraulic liquid can flow from each of the channels over and between each of the edge portions, with the valve body positioned within the valve housing to allow liquid to flow into and out of the hydraulic chamber. And the edge portion in the second position of the valve body interacts sealingly. As such, it is characterized by the inability of hydraulic fluid to flow into or out of the hydraulic chamber.

The solution according to the invention results in a very short flow path, which allows a very immediate treatment. Furthermore, according to the invention, it is also possible to control the hydraulic piston independently of the position of the hydraulic piston. In this connection, it is advantageous to form the valve body as a sleeve-shaped means, whereby a large flow opening can be achieved with a relatively small movement.

It is understood that the present invention allows a solution with all the advantages obtained to be used in many different applications.

According to a further possible aspect of the invention, the edge portion of the valve body is at least one integral part of the opening, the valve body being essentially relative to a plane running centrally over the valve body. Formed symmetrically, the maximum required movement of the valve body in the valve housing for moving the valve body from the closed position to the open position is between 0.1 and 3% of the outer diameter of the sleeve, preferably Is less than 2%, more preferably less than 1%, the movement of the valve body between the closed position and the open position is at least substantially carried out axially with respect to the hydraulic piston, The time for adjusting the body from one end position to the other end position is less than 10 ms, preferably less than 5 ms, the hydraulic piston being provided with at least two annular force transmitting surfaces. , This pair with each other Facing, preferably the upper annular surface is larger than the other, the hydraulic piston comprises three coaxial integrated units with different outer diameters,
The central portion has a maximum diameter, at least one control mechanism is hydraulically actuated, the control mechanism comprises means arranged to be able to move the valve body,
This means is movable within an opening in the valve housing, the opening essentially corresponding to the shape of said means, said opening communicating with an annular channel intended to be pressurized by hydraulic oil. The means has a circular outer jacket surface, the opening consisting of an axially extending circular hole, the control mechanism is magnetically actuated, the control mechanism is provided in the valve body At least one ferromagnetic part and at least one electromagnet provided on the valve housing, the electromagnet being cooled by hydraulic oil, the valve housing being provided on one or several of its side walls, A pressure connection and a tank connection are provided, the device is part of an impact / pushing means intended to carry out an immediate impact and transmit a heavy force, the valve body having a minimum diameter between 3 and 500 mm. Existence Preferably 50 mm or more, more preferably 80 mm or more, and-at least one of said edge portions-provided with symmetrically arranged recesses, whereby with a small movement of the valve body from its closed position, A small radial flow can be generated through the valve body, the length of the rim and thus the total area of the opening may be varied by changing the position of the valve body rotationally, The valve body is positioned by the hydraulic pressure acting on the annular surface, hydraulic fluid to at least one of said surfaces being controlled by a valve slide provided on the valve body and working according to the known principle of copying a valve, so that The surrounding valve body blindly follows the valve slide, which in turn is positioned by the double-acting electromagnet, the hydraulic piston being less than the hydraulic chamber. Also provided an end face facing one of the outer hydraulic piston is located inside the valve housing coaxially formula, - two separate hydraulic chambers are provided in the valve housing.

[0011]   The present invention will be described in more detail with reference to the accompanying drawings.

FIG. 1 shows a hydraulic impact / push device according to a first embodiment of the invention, which embodiment is particularly suitable for carrying out long impact movements. The device comprises a valve housing 1, a hydraulic piston 3 arranged in the center of the valve housing, a valve body 2 arranged inside the valve housing 1 but surrounding the hydraulic piston, and a control mechanism 4.

The valve housing 1 comprises a plurality of assembled parts, the upper cap 101
It comprises a top portion 102 arranged (not shown). An inner valve seat portion 103 and an outer valve seat portion 104 are connected to the lower end of the upper portion 102. The above two parts 1
At the lower end of 03, 104 is a lower common cap 106. In the center, along the central axis of the valve housing 1 is an upper circular cavity 116, i.e. a first hydraulic chamber, in which the hydraulic piston 3 is provided. The circular cavity 116 has a diameter adapted to the central portion 34 of the hydraulic piston, which portion exhibits the largest diameter of the hydraulic piston. Above the central portion 34 of the hydraulic piston, there is an upper portion 35, the diameter of which is smaller than the diameter of the central portion 34, so that an annular upwardly facing surface 30 is formed. The surface 30 is a power transmission surface for hydraulic oil, which is pressurized in an annular slot extending between the upper portion 35 of the hydraulic piston and the inner jacket surface of the valve housing.

Essentially the inner jacket surface 134 of the inner valve seat portion 103 comprises the upper portion 1
02 has the same diameter as the central cavity 116, which allows the hydraulic piston 3
With the central portion 34 along with a central cavity 115 forming a second hydraulic chamber inside the inner valve seat portion 103. The lower part 33 of the hydraulic piston 3 has a smaller diameter than the upper part 35. In this way a downwardly facing annular surface 33 is formed, the surface of which is larger than the upwardly facing annular surface 30. The surface 30 has an axial channel 129 and a radial upper channel 1.
A constant pressure is applied via 24 via the pressure inlet 107. A circular opening is provided in the lower part of the inner valve seat part, the diameter of which is the lower part 33 of the hydraulic piston.
Of diameters, so that there is substantially an interference fit therebetween. leakage(
In order to minimize (not shown) some sealing is preferably provided on said part and a good fit is provided on the other part. Outer part of valve seat 10
4 has at least one inlet 107 for hydraulic liquid and one outlet 119 for hydraulic liquid. Directly connected to the inlet 107, there is an annular channel 151 (
See FIG. 2). The outer valve seat portion 104 is connected to the annular channel 151.
There is a slotted cylindrical space 128 between and the inner valve seat portion 103, this space being for the valve body 2. On the opposite side and on the other side of the slit 128, an additional annular chamber 150 is provided in the inner valve seat portion 103.

Below the annular chamber 151, between the inlet 107 and the outlet 119, an annular portion with a sharpened inwardly directed edge is provided on the outer valve seat portion 104 to provide an upper sealing annular corner / edge. A portion 104A and a lower sealing annular corner 104B are formed. Correspondingly, within the slotted space 128 and opposite the annular corner / edge portion, an annular edge portion is formed in the inner valve seat portion 103 through the upper annular edge portion 103A and the lower annular edge portion 103B. It The annular corner edge portions 103A, 103B, 104
A, 104B interacts with the axially moveable valve body 2 and the openings 250, 251, 252 therein to achieve the desired adjustment. Also, the center of the opening is made up of a plurality of openings (see FIG. 2). Upper opening 25 of valve body 2
The 0 and lower openings 251 are each provided in multiples to allow free hydraulic flow in a balanced manner. Also, the center of the opening is made up of a plurality of openings (see FIG. 3). The openings 252 are preferably provided with straight lower and upper edges to allow more efficient interaction with the corner / edge portions. The channels 152, 155 and the opening 251 are in the tank 119
Are arranged in the same way for the outlets to the outlet, so that in principle the openings 153
There is a mirror symmetry around plane P1 which runs through the center of to the lower pressure chamber 115. An iron ring 41 is attached to the lower end of the valve body 2. Below the iron ring and coaxially thereto, one (or more) electromagnet 42 is provided for controlling the valve body 2. The valve body has a small annular surface 207 on its upper portion.
This annular surface 207 is also provided, which means that an upwardly directed force always acts through the annular surface 207 when pressure acts inside the chamber 151. Due to the limited movement demands, the control / movement of the valve body 2 can be magnetically generated advantageously.

A plurality of axially arranged channels 129 are provided for the pressure chamber 151.
Is connected to an upper annular cavity 116 in the valve housing 1, which channel is routed via a radial bore 124 in the upper portion of the valve housing 1 to the annular opening / slit 1.
Enter in 16.

The valve functions as follows. In the position shown in FIG. 1, the oil movement does not occur in either direction, but the hydraulic piston 3 is in a balanced position and the oil carried through the channel 129 presses against the upper surface 30. And
This is balanced by the oil contained inside the lower chamber 115,
It acts via the downwardly facing annular surface 31. When the piston remains stationary in this way, the position of the equilibrium position may be adjusted arbitrarily and thus depends on the amount of oil contained in the lower chamber 115. If an increased voltage is applied to the electromagnet 42, it exerts a force via the iron ring 41, which pulls the valve body 2 downwards. When this happens, the opening has two lower annular edges 104B,
103B, the valve body 201, and the edge of the central opening 252, so that oil can be drawn from the lower annular space 115 into the openings / channels 153, 154.
, 252 into the annular channel 152 and then out further through the outlet 119 to the tank. At the same time, the upper annular edge portions 104A, 103
A seals the valve body 201, so that the pressure chamber 151 through the inlet opening 15
There is no oil flowing down 4 into the inner annular chamber 115. On the one hand, the axial channel 129 and the annular upper chamber 1 acting towards the upper annular surface 30
A constant oil pressure is maintained via 16 radial channels 124.
This therefore directs the piston movement in the downward direction and therefore its lower end surface 3
2 can move downwards and make strokes. Since the total area of the upper surface 30 is larger than the area below and inside it of the lower surface 31, the stroke is stronger in the downward direction than in the upward movement. again,
The central opening 252 of the valve body is properly designed with a flat upper and lower surface so that slight movement of the valve body will leave the chamber 115 at the outlet 119.
This means that the opening exposed to the oil moving towards will change significantly.

According to the embodiment shown, the outer diameter D of the valve body is 100 mm, which gives a very large flow opening for movement when the valve body moves only 1 mm. The total surface reaches approximately 600 mm ² because the edge portions extend in all directions (D × π × 1 mm when using two edges). When the impact movement (or pressing) is completed (or the desired position is reached), the current supply to the electromagnet 42 is terminated (decreased), so that the pressure acting on the surface 207 of the valve body 2 exerts a magnetic force. Overcome, which causes the valve body to move rapidly upward. In this way, an opposite oil flow occurs, forming an opening between the upper annular edge portions 104A, 103A and the valve body 201. Thus, the oil in the pressure chamber 151 is thereby free to flow down through the opening 252 in the valve body and further into the annular chamber 154, through it and then through the radial opening 153. And flow into the lower annular pressure chamber 115. As a result of the increased pressure in the lower annular chamber 115 (which pressure is the same as in the upper annular chamber 116), the piston moves upward and the lower annular surface 31 has a much larger surface than the upper annular surface 30. When the return movement has taken place to the desired position, the control mechanism is activated again, allowing a new impact (or push) as described above. If, instead, the device is used as a regulating means, the current supply to the electromagnet only changes to such an extent that the valve closes (position according to FIG. 1) and the piston 3 stops at the desired position. .

Since the radially exposed surface of the valve body is exposed as a large counter-force on the opposite side of the valve body 2 at all selected points, the valve body is always radially balanced. It must be noted that it is a state. This is achieved by virtue of an annular recess and an opening in the valve body that are symmetrically made around the valve body, which allows communication between the annular spaces. As already mentioned in the introduction to the description of FIG. 1, the above embodiment is particularly advantageous for devices with long strokes.

The preferred embodiment according to FIG. 4 shows many essential similarities to the embodiment according to FIG. 1, but is more suitable for short and quick movements. The first important difference is that it does not pressurize constantly in either direction, but uses alternating pressurization to affect this around the piston in one direction or the other. Another important fundamental difference is that the valve body 201 according to this embodiment is magnetic in its own right and thus does not require an extra iron ring 41, but electromagnets 42A, 42 on each side of the valve body 2.
B (two) can be used to control the position of the valve body 2. A further difference is that there are two outlets 119A, 119B running into the tank. The basic principle of how the structural details interact in the previously described embodiment according to FIG. 1 and in the embodiment shown in FIG. Only "one half" is described below. This is done considering piston movement in only one direction. But first, a further difference to the embodiment according to FIG. 1 is explained. The valve housings 104, 103 and the valve body 2 are each provided with four pairs of annular rim means arranged in pairs, only two of which interact to open and the other two pairs of which are closed. Interact with each other. Below is one to one
Only 03A, 104A and 103C, 104C each interact (as open) as the piston 3 makes a downward stroke. As in the embodiment according to FIG. 1, the valve body 2 has a plurality of centrally provided openings or openings 2.
There is 52. The openings are for pressure balancing and achieving a quick and short flow path (see also Figure 7). Furthermore, it is also shown that there are multiple inlets for the hydraulic liquid 107. It is also shown that there is an annular recess 260 in the inner jacket surface of the valve body 2 in order to achieve the pressure balance in the central plane P1.
On each side of the row of central openings 252 of the valve body 2, symmetrically with respect to the central plane P1, the valve body 2
Are each provided with a plurality of radial openings 261 and 262 (see also FIG. 6). The openings form communication between outer annular chambers 163 and 164 provided in the outer valve seat portion 104 and inner annular chambers 161 and 160 arranged in the inner valve seat portion 103, respectively. Inside chamber 1
60 and 161 communicate with openings 124 and 153, respectively, and run to respective pressure chambers 115 and 116. Finally, the valve body is provided with an additional set of radial openings 263 and 264, which are arranged symmetrically in said plane P1 and are provided with an inner annular chamber 162 and an upper annular chamber 165, respectively. The lower and upper annular chambers are in direct communication with lower and upper outlets 119A and 119B, respectively, which run into the tank (see also Figure 5).

The device according to the preferred embodiment shown in FIG. 4 functions as follows. Pressure is via multiple inlets 107 (of course only one inlet may be used)
, Thus pressurizing the annular chamber 151 in communication with the central opening 252 of the valve body 2. Once the position according to FIG. 4 has been reached, no movement of the hydraulic piston occurs in either direction, all flow paths from the annular chambers 151 and 260 are sealed and the edges slightly overlap each other. When electric current is supplied to the upper electromagnet 42 in this manner, the magnetic field moves the valve body 2 in the upward direction as shown in the drawing. In that regard, the annular edges 271A, 271B and 272A of the valve body along the entire edge line.
, 272B, an opening is formed between the edge portions 104, 27B.
It may flow between the annular slits formed between 1B and 103A, 271A and upward from the central annular chambers 151 and 260, respectively, into the two upper annular chambers 161 and 163. From here, the pressurized oil is then
It may freely flow into the inner upper annular chamber 116 via the radial openings 124 and then pressurize the piston downward via the upper surface 30. At the same time, the corresponding slits 104C, 272A and 103C, 272B, respectively, open at the bottom and the oil emerges from the lower annular pressure chamber 115 and flows through the radial opening 153 into the annular chamber 160, directly therethrough. Through the inner annular slit 160 or through the opening 261 of the valve body 2 and down through the other annular slit 164 into the lower annular chamber 162 and exit 1
Exit through 19A and go to the tank. Thus, pressurization of the upper annular chamber 116 occurs instantaneously, while draining of the lower annular chamber 115 is performed. As a result of this process, the piston 3 may perform a rapid downward movement and the piston end surface 132 may then make a strong stroke. When the stroke is thus carried out by the lower magnetic device 42A, the movement of the valve body 2 is reversed and the opposite pressurization and drainage occur respectively, so that the piston moves upwards instead. The unbroken interaction edges, eg 104C and 272A, mean that a very small movement of the valve body 2 leads to a large opening, i.e. a large annular slit is formed so that a large flow may be achieved. Should be noted. Thanks to the provision of the surface 30 (instead of using the end face of the piston 3), a relatively small change in volume is achieved when the piston moves in either direction, which further improves the speed of the device. Should also be noted. However, it should be noted that the device is not limited to the two end faces of the piston which have to project from the valve housing 1. Furthermore, as can be seen from the cross section, the valve housing
It is also advantageous to be designed with a rectangular outer shape.

FIG. 8 shows an additional embodiment of the hydraulic system according to the present invention. As the basic principle is roughly the same as the above embodiment, only the essential differences will be discussed below. The first important difference is that the valve body 2 according to this embodiment is not totally balanced. Thus, when the inlet 107 for pressurized liquid is constantly pressurized, the valve body will, to some extent, press the central protruding portion of the inner seat portion 103, so that if very high accuracy is required, This device is not very suitable as a servo valve. However, the most important difference is the control mechanism 4 for movement of the valve body 2. According to this embodiment, the use of the hydraulic control mechanism 4 is shown. This is accomplished by the fact that a plurality of projecting means 280 and 290 are provided on each side of the valve body 2, namely on the upper side and the lower side, which means press the valve body in both directions. Suitably, they are circular and run sealingly within circular lumens 122 and 125 in the valve housing 1, respectively. By providing annular channels 123 and 126 for the lumens 122 and 125, respectively, alternating pressurization of the annular channels can affect the valve body 20 and allow it to move in both directions. The pressurization of the annular channels 123 and 126 has inlets 132A, respectively, to have a connection in the vicinity of each other.
And 132B as appropriate. However, it is preferably not coplanar (the drawings show this only to more clearly illustrate the function). Thus, there is an axial channel 127 and 130 from each inlet of the control mechanism which runs via radial lumens 121A and 121B to the annular channels 123 and 126, respectively. Therefore, it should be noted that the radial lumens 121A and 121B must be plugged at the ends so that oil does not flow out of the valve housing 1. Similar to FIG. 4, an embodiment is shown in FIG. 8 in which one of the two chambers is alternately pressurized and the unpressurized chamber is drained by connecting to a tank.

A graph is shown in FIG. 9, which clarifies the effect of the embodiment improving the controllability of all applications, the surrounding valve acting as a servo valve, ie for positioning the hydraulic piston. belongs to. As an example, reference is made to the bottom of FIG. 1, but it should be understood that the principles are used in other embodiments. The effect is achieved, for example, by making the edges 103A, 103B, 104A, 104B, which treats the opening of the oil flowing into the partially chamfered annular ring area (eg 154) and therefore the first Center position during exercise, eg about 0.2
mm to the edge of the opening only comprises, for example, 10% of the circumference and is about 0.2
After said opening movement of mm, the valve can open around the entire circumference. In this way, more precise control is achieved at low speed (or stop), and the small flow makes the control process quieter. In addition, leakage decreases along the long circumference.
The edge changes are carried out symmetrically, so it is important that they are well balanced. It will be appreciated that there are many alternatives to the chamfer in the edge portion, for example indentations symmetrically arranged in the edge region.

FIG. 10 shows an additional embodiment / modification of the invention in which the surrounding valve sleeve 2 incorporates a copy valve mechanism. The basic principles and design of the hydraulic system are essentially the same as those described above, so many of the designations shown in FIG. 10 have already been described in connection with the above figures. Therefore, in the following, only the essential changes will be focused. Furthermore, only one limited part of such a hydraulic system is shown, for example the hydraulic piston or bottom plate is not shown, and the principle of the above details and other necessary peripheral details are as described above. It is the same. In principle,
Similar to the one described above, a double-acting electromagnet is used to influence / control the valve device, but in this case via the copy valve bar 41A. Other details of the portion forming the copy valve mechanism will be described in more detail with reference to FIG. The vertical channel 298 is provided through the movable valve sleeve 2, so that the lower pressure, which corresponds to the outlet pressure to the tank (T), is on the upper side of the slotted space 128, in which the valve sleeve 2 is located. Move. As shown in FIG. 11, the sleeve-shaped lining 291
Is provided and is fixedly provided inside the valve sleeve 2. The diameter of the longitudinal opening inside the lining 291 is the same as the diameter of the copy valve bar 41A (with a certain degree of fitness). At the position shown, the copy valve bar 41A has its upper end 41C.
Together, it extends over the upper edge portion 291A of the lining. In the space between the upper edge portion 291A of the lining and the lower edge portion 291B of the lining, the bar 4
1A is provided with a narrower web 41B so that a sealing edge is formed at both the lower edge portion 291B and the upper edge portion 291A of the lining with respect to the edge portion at the end of the web 41B. An opening 295 extending in the radial direction is provided in the middle of the lining, which opening surrounds the lining 291 with a slotted space 29.
Connect to 2. The space 292 then communicates with the annular channel 293 via the opening 294 in the valve sleeve 2. Since the pressure P in the surrounding chamber acts on the surface Ai of the valve sleeve 2, the valve sleeve 2 aims to move upwards. The pressure is thus transmitted via the channel 107, but the copy valve bar 41A
And the lower edge of the lining 291 is also reached via the slotted space between the valve sleeve 2. As already mentioned, the lower tank pressure T is on the upper side of the lining 291. When the copy valve bar 41A moves upward, the hydraulic chamber 29
3 is connected to the tank T via an upper slotted space 128, which is
It always has a low pressure T via the channel 298. When the copy valve bar 41A moves downward with respect to the valve sleeve 2, the hydraulic chamber 293 causes the channel 107 to move.
The pressure P is applied via. The pressure affects the surface Ay of the valve sleeve 2,
It is provided inside the hydraulic chamber 293. The surfaces Ay are facing upwards and are larger than the surfaces Ai facing downwards, thus these surfaces are
A component force is applied in the opposite direction (F = p × A), preferably Ay = 2 × Ai. Therefore, the pressure inside the chamber 293 depends on the direction in which the oil flows.
Low pressure T via the sealing edge 291A or the sealing edge 2 depending on whether it flows in
One of the higher pressures P via 91B, which in turn is the inner opening 2
95, transmitted to the channel 292 and finally through the outer opening 294, so that the valve sleeve 2 moves in the same direction as the movement of the valve bar 41A, eventually its balance position is reached by the valve edges 291A, 291B, The web 41B again closes each sealing edge and thus a copy of the movement of the valve bar is achieved.

FIG. 12 shows an alternative embodiment of the device according to the invention, it being clear that the valve device does not necessarily have to have the hydraulic piston 3 located inside the valve housing. In many applications, it may in fact be desirable to so separate the valve housing 1 and the hydraulic piston / cylinder. The principle of valve function is exactly the same as described with reference to FIG. Therefore, although the same indicia as in FIG. 4 are used, certain parts of the device according to FIG. 12 are shown more schematically. Therefore, in the following, only the differences from FIG. 4 will be focused. As described above, the hydraulic piston 3 is not provided inside the valve housing 1. Instead, the central portion 10
3E is formed as a homogeneous unit. The lower pressure chamber 115 has an outlet 115
In communication with A, which is connected to a conduit, preferably to a hydraulic hose 115B leading to a corresponding lower pressure chamber of a hydraulic cylinder (not shown), which is provided with a hydraulic piston 3 (not shown). . The hydraulic piston 3 and the cylinder are in principle generally appropriately designed in a conventional manner, the design according to the application being adapted to the desired functional pattern, for example the hydraulic piston 3 having a functional pattern according to any of the embodiments described above. give. In a corresponding manner, the upper pressure chamber 116 is connected to the upper outlet 116A, which is preferably connected to the upper hydraulic conduit 116B and is also a hydraulic hose, which runs to the corresponding upper hydraulic chamber inside the hydraulic cylinder, Is provided with a hydraulic piston 3. In this way, the function is identical to that described with reference to FIG. 4, except that the hydraulic cylinder with the hydraulic piston 3 is arranged at a distance from the valve housing 1. Furthermore, it can be seen from FIG. 12 that the valve sleeve 2 may advantageously be designed with the same or at least approximately the same wall thickness along the entire extension.

FIG. 13 has a hydraulic piston 3 coaxially provided inside the valve housing 1,
A preferred embodiment of the valve device according to the invention is shown in which a constant pressure is used for one pressure chamber. Unlike that shown in FIG. 1, according to this preferred embodiment, the constant pressure is applied to the lower chamber 115. The above embodiment is shown in FIG.
In some respects, it is quite surprising, suggesting a considerable advantage over the sequence according to. The design principles of the valve housing 1 and the valve body 2 are essentially the same as described above and will not be described in detail with reference to this drawing. On the other hand, the hydraulic piston 3 is designed differently so that the upwardly facing surface 30 of the upper annulus is the annular surface 3 of the opposite direction.
Essentially greater than 1. The hydraulic piston is provided inside the valve housing 1, so that the smaller surface 31 is inside the lower pressure chamber 115, which always communicates with the pressure inlet 107 via the channel 153 of the inner valve seat portion 103. The upper chamber 116 depends on the position of the valve body 2 according to the principles described above, through the channel 124 of the inner valve seat 103, the pressure inlet 107 or the outlet 1 to the tank.
19 or block the communication altogether.

In FIG. 14, the device according to FIG. 13 is schematically shown in order to explain the functional principle more simply. It is shown that the valve housing 1 is advantageously provided with sealings S1, S2, S3 in order to seal the pressure chambers 115, 116 from each other and from the surroundings. Furthermore, the valve body 2 is shown as a separate unit provided outside the valve housing. However, this is a principle drawing and does not limit the present invention in any way, and it is an integral valve body 2 or an externally arranged valve unit 2
It should be understood by those skilled in the art that can be used to take advantage of the device according to this preferred embodiment. The valve means 2 is spring-loaded in one direction (tension spring), so that the external influence is in the position shown in FIG. 14, namely the conduit L3 via the first connection V1 of the valve means 2 (inside the valve housing) Position via the conduit L2 (which may also be partly inside the valve housing) to connect the channel 124 near the upper pressure chamber 116 to the pressure source P. Shown to take. It is advantageous from a safety point of view that the spring positions the valve 4 so that the upper chamber is not pressurized without any external influence. As can be seen from the figure, the pressure source P is provided with an accumulator tank PA, which keeps the pressure in the pressure conduit L2 always at the desired level. As shown in FIG.
The piston is affected by a downward force that is essentially greater than the upward force, resulting in a rapid downward acceleration. If the position of the valve means 2 then changes so that the upper conduit L3 communicates with the conduit L4 to the tank T via V2, this upper chamber 116 will have an essentially low pressure. Since there is always full system pressure in the lower pressure chamber 115, the hydraulic piston 3 is then subjected to an upwardly directed acceleration force, so that the hydraulic piston carries out a return stroke. However, the upwardly facing pressure surface 30 is
Since it is more than twice as large as one, the acceleration of the return stroke is not as great as the impact movement. This arrangement has the very important advantage that essentially less oil is required when it is ejected from the lower pressure chamber 115 in an impact movement than when used in the arrangement according to FIG. can get. Further, the return oil from the lower pressure chamber 115 is routed through L1, V1 and L3 to the upper chamber 11
6 has the advantage that there is no back flow into the tank due to the stroke. This reduces the required capacity of the hydraulic system and eliminates the need for large return conduits to absorb the heavy backflow that would otherwise occur. Another obvious advantage is that the safety is greatly improved. Whenever a piston is used, it is always pressurized in the upper pressure chamber 116, and there is always the risk of a high-energy stroke if any defect in the device appears. Alternatively, the risk is eliminated if the striking piston is constantly pressurized on the bottom side, as shown according to the preferred embodiment of FIGS. 13 and 14. Furthermore, by arranging double the number of valves and connecting them to the tank on the upper side of the piston, more protection against malfunction is obtained. Also, referring to another aspect, the embodiment according to FIGS. 13 and 14 provides improved safety, ie the risk of diesel combustion is avoided. In connection with the device according to FIG. 1, a large oil column is actually accelerated in stroke, which rapidly leaves the lower chamber 115 when the piston suddenly delays during operation, which in the course of milliseconds. Implied that there may be oil loss in the lower chamber, resulting in negative pressure. This implies that a component not manufactured for negative pressure, eg a pressure sensor, fails. In addition, sealings made from flexible materials can be damaged and are subject to leakage due to negative pressure, ie pit damage. Negative pressure also means that the oil opens the boundary air. Free bubbles are then formed, which can subsequently ignite when the pressure rises, ie diesel combustion, which at best only ignites the oil and the ceiling. All these drawbacks are eliminated in the embodiment according to FIGS. 13 and 14, so that in the striking movement very few oil columns are ejected from the chamber 115. As mentioned above, this principle of achieving a rapid striking movement in connection with the processing at high speed is not limited to a device with a valve body 2 according to the preferred embodiment described above, which principle is of the field. It is understood that it may be used in connection with essentially any type of external valve device that is quick enough to meet the requirements within the application.

The invention is not limited to the above description, but may vary within the scope of the claims. For example,
The principle of functioning of the hydraulic system can also be achieved by a turned / rotated valve body, instead of moving axially. Subforms, such as spiral movements, may also be contemplated. In the movement of turning the valve body, an electromagnet is used, for example in the same manner as an electric engine, to fix the rotor, preferably to the sleeve, and to a set of permanent magnets, suitably with radial magnetic flow, to the stator on the valve housing. It is moved properly by fixing. Suitably any type of angle sensor is provided on the sleeve. With such a solution it is possible to control the position of the valve body arbitrarily and thus the position and operating mode of the hydraulic system.

[Brief description of drawings]

[Figure 1]   FIG. 1 is an axial sectional view showing a first embodiment of a hydraulic system according to the present invention.

[Fig. 2]   FIG. 2 is a cross-sectional view taken along the line AA of FIG.

[Figure 3]   FIG. 3 is a sectional view taken along the line BB of FIG.

FIG. 4 is an axial cross-section of a preferred embodiment according to the invention which is particularly suitable for immediate movement.

[Figure 5]   FIG. 5 is a cross-sectional view taken along the line AA of FIG.

[Figure 6]   FIG. 6 is a cross-sectional view taken along the line BB of FIG.

[Figure 7]   FIG. 7 is a cross-sectional view taken along the line CC of FIG.

[Figure 8]   FIG. 8 is an axial cross-section showing an alternative embodiment of the device according to the invention.

[Figure 9]   FIG. 9 is a graph showing the effect of the preferred embodiment of the present invention.

[Figure 10]   FIG. 10 is a diagram of an alternative embodiment according to the present invention.

FIG. 11   FIG. 11 is an enlarged view showing certain details of FIG.

[Fig. 12]   FIG. 12 is an axial cross-sectional view showing a modified hydraulic device according to the present invention.

13 is a diagram showing a preferred embodiment of a hydraulic system according to the principle of the device shown in FIG.

FIG. 14   FIG. 14 shows a preferred functional principle of the device according to FIG.

─────────────────────────────────────────────────── ─── Continued front page    (81) Designated countries EP (AT, BE, CH, CY, DE, DK, ES, FI, FR, GB, GR, IE, I T, LU, MC, NL, PT, SE, TR), OA (BF , BJ, CF, CG, CI, CM, GA, GN, GW, ML, MR, NE, SN, TD, TG), AP (GH, G M, KE, LS, MW, MZ, SD, SL, SZ, TZ , UG, ZW), EA (AM, AZ, BY, KG, KZ, MD, RU, TJ, TM), AE, AG, AL, AM, AT, AU, AZ, BA, BB, BG, BR, BY, B Z, CA, CH, CN, CO, CR, CU, CZ, DE , DK, DM, DZ, EE, ES, FI, GB, GD, GE, GH, GM, HR, HU, ID, IL, IN, I S, JP, KE, KG, KP, KR, KZ, LC, LK , LR, LS, LT, LU, LV, MA, MD, MG, MK, MN, MW, MX, MZ, NO, NZ, PL, P T, RO, RU, SD, SE, SG, SI, SK, SL , TJ, TM, TR, TT, TZ, UA, UG, US, UZ, VN, YU, ZA, ZW [Continued summary] This edge (272A, 272B) is provided on the valve Edge portions (103C, 10C) located inside the housing (1) 4C) and channels (160, 164) The hydraulic liquid from each of the channels Can flow over and between each of the sections, The valve body (2) is positioned inside the valve housing (1) when Liquid to the hydraulic chamber (115) and To allow flow from these and of the valve body (2) The edge portion in the second position interacts to seal Therefore, the hydraulic liquid is transferred to the hydraulic chamber (115). Can't flow to or from now on.

Claims (21)

[Claims] 1. A valve housing (1) comprising a movable valve body (2) arranged inside the valve housing, at least one hydraulic chamber (115) provided inside the valve housing (1), At least one for controlling the movable valve body (2)
A hydraulic system comprising one control mechanism (4), the valve housing (1) comprising a plurality of combined elements (102, 103, 104), at least two of the elements (103, 104). 104) are arranged coaxially with respect to each other, so that an annular space (128) is formed between the two parts, the valve body (2) being substantially sleeve-shaped and the valve housing (128). Arranged within the annular space (128) within 1), the valve body (2) has a plurality of openings to allow hydraulic liquid to flow radially through the valve body (2). (250, 251, 252, 206
, 202) are provided, the valve housing (2) being essentially, preferably totally balanced, against the hydraulic pressure acting in the radial direction. 1) Inside, the valve body adjacent the opening is provided with edge portions (272A, 272B) on both the inner and outer surfaces of the valve body, the edge portions (272A, 272B). Interact with the edge portions (103C, 104C) and channels (160, 164) provided inside the valve housing (1) so that hydraulic fluid flows from each of the channels and over each of the edge portions and In the meanwhile, the valve body (2) then flows into the valve housing (1
) Positioned internally to allow liquid to flow to and from the hydraulic chamber (115), and the rim portion of the valve body (2) in the second position interacts sealingly, As a result, the hydraulic system is characterized in that the hydraulic liquid cannot flow to or from the hydraulic chamber (115). 2. Device according to claim 1, characterized in that the edge portion of the valve body (2) is an integral part of at least one of the openings. 3. Device according to claim 1, characterized in that the valve body (2) is designed essentially symmetrical with respect to a plane (P1) running centrally over the valve body. 4. The maximum required movement of the valve body (2) within the valve housing (1) to move the valve body (2) from the closed position to the open position is the outer diameter (D) of the sleeve. 2. The device according to claim 1, characterized in that it is between 0.1 and 3%, preferably less than 2%, more preferably less than 1%. 5. The movement of the valve body (2) between a closed position and an open position is performed at least substantially axially with respect to the hydraulic piston (3). 1. The device according to 1. 6. The time for adjusting the valve body (2) from one end position to the other end position is less than 10 ms, preferably less than 5 ms. The device according to. 7. A hydraulic piston is provided in the hydraulic chamber with at least one outwardly facing end surface (32), the hydraulic piston (3) being coaxial with the interior of the valve housing (1). The device of claim 1, wherein the device is arranged. 8. The hydraulic piston (3) comprises three coaxial integrated units (33, 34, 35) having different outer diameters, the central portion (34) having the largest diameter. The device according to claim 7. 9. Device according to claim 1, characterized in that at least one control mechanism (4) is hydraulically actuated. 10. The control mechanism (4) comprises means (280, 290) arranged to be able to move the valve body (2), the means being within the valve housing (1). Can move within the openings (122, 125) and
122) essentially corresponds to the shape of the means, characterized in that the opening (122, 125) communicates with an annular channel (123, 126) intended to be pressurized by hydraulic oil. The device according to claim 9. 11. The means (280, 290) has a circular outer jacket surface and the opening (122, 125) is an axially extending circular hole. The device according to. 12. The device of claim 1, wherein at least one control mechanism is magnetically actuated. 13. The control mechanism (4) comprises at least one ferromagnetic portion (41) located in the valve body and at least one electromagnet (42) provided in the valve housing. 13. The device according to claim 12, characterized in that 14. Device according to claim 13, characterized in that the electromagnet (42) is cooled by hydraulic oil. 15. Device according to claim 1, characterized in that the valve housing (1) is provided with a pressure connection (107) and a tank connection (119) on one or several of its side walls. . 16. The device is part of an impact / pushing means intended to perform an immediate impact and transmit a heavy force, the valve body (2) being between 3 and 500 mm.
Device according to claim 1, characterized in that it has a minimum diameter between, preferably 50 mm or more, more preferably 80 mm or more. 17. At least one of said edge portions is provided with symmetrically arranged depressions whereby a small movement of said valve body (2) from its closed position causes said valve body (2) to move. A device according to claim 1, characterized in that a small flow can be generated in the radial direction through 18. The device of claim 1, wherein the length of the edge portion, and thus the total opening area, may be varied by changing the position of the valve body in a rotational direction. 19. A valve provided on the valve body (2), wherein the valve body (2) is positioned by hydraulic pressure acting on an annular surface (Ai, Ay) and hydraulic fluid to at least one of the surfaces. It is controlled by a slide (41A) and operates according to the known principle of copying a valve, so that the surrounding valve body is said valve slide (4A).
1) The device according to claim 1, characterized in that it follows blindly and is positioned by a double-acting electromagnet. 20. The hydraulic piston (3) is provided with at least two annular force transmission surfaces (30, 31) facing each other, preferably an upper annular surface (
Device according to claim 7, characterized in that 30) is larger than the other. 21. Device according to claim 1, characterized in that the valve housing (1) is provided with two separate hydraulic chambers (115, 116).